Rotary heat engine powered two fluid cooling and heating apparatus

ABSTRACT

Rotary closed Rankine cycle cooling and heating apparatus utilizing separate engine power fluid and refrigerant fluid. The apparatus includes a rotary boiler, power fluid expander and condenser coupled with a refrigerant compressor, refrigerant expander and refrigerant evaporator. The components are disposed on a common axis with the condenser and evaporator axially spaced and the boiler, power fluid expander, refrigerant compressor and expander compactly arranged in a housing between the condenser and evaporator. The housing, condenser and evaporator are mounted for coaxial rotation together as a unit. The power fluid expander is driven at a predetermined speed by pressure power fluid generated in the boiler and in turn drives the refrigerant fluid compressor. The refrigerant expander is of the capillary type constructed and arranged with respect to the evaporator to automatically control the capacity balance of the refrigerant system. The entire unit is hermetically sealed and the Rankine cycle power system is adapted and designed for use with high molecular weight fluids. In one disclosed embodiment of the invention the rotary housing-condenser-evaporator unit is rotationally driven at constant speed by the power fluid expander through an internal occluded fixed-ratio gear train and torque anchor, and in another disclosed embodiment, the housingcondenser-evaporator unit is rotationally driven at constant speed by an external motor and the power fluid expander drives an internal alternator that provides electric current for the external drive motor and other electrical equipment.

United States Patent Doerner 1 Feb. 4, 1975 ROTARY HEAT ENGINE POWEREDTWO FLUID COOLING AND HEATING APPARATUS [75] Inventor: William A.Doerner, Wilmington,

Del.

[73] Assignee: E. I. du Pont de Nemours and Company, Wilmington, Del.

[22] Filed: Aug. 8, 1973 [21] Appl. No.: 386,630

Related US. Application Data [63] Continuation-impart of Ser. No.316,851, Jan. 2, 1973, which is a.continuation-in-part of Ser. No.227,902, Feb. 22, 1972, abandoned.

Primary ExaminerMartin P. Schwadron Assistant Examiner-Allen M. OstragerAttorney, Agent, or Firm-Howson and Howson [57] ABSTRACT Rotary closedRankine cycle cooling and heating apparatus utilizing separate enginepower fluid and refrigerant fluid. The apparatus includes a rotaryboiler, power fluid expander and condenser coupled with a refrigerantcompressor, refrigerant expander and refrigerant evaporator. Thecomponents are disposed on a common axis with the condenser andevaporator axially spaced and the boiler, power fluid expander,refrigerant compressor and expander compactly arranged in a housingbetween the condenser and evaporator. The housing, condenser andevaporator are mounted for coaxial rotation together as a unit. Thepower fluid expander is driven at a predetermined speed by pressurepower fluid generated in the boiler and in turn drives the refrigerantfluid compressor. The refrigerant expander is of the capillary typeconstructed and arranged with respect to the evaporator to automaticallycontrol the capacity balance of the refrigerant system. The entire unitis hermetically sealed and the Rankine cycle power system is adapted anddesigned for use with high molecular weight fluids. In one disclosedembodiment of the invention the rotary housing-condenser-evaporator unitis rotationally driven at constant speed by the power fluid expanderthrough an internal occluded fixed-ratio gear train and torque anchor,and in another disclosed embodiment, the housing-condenser-evaporatorunit is rotationally driven at constant speed by an external motor andthe power fluid expander drives an internal alternator that provideselectric current for the external drive motor and other electricalequipment.

31 Claims, 11 Drawing Figures PATENTEB FEB 4I975 sum 2 or s PATENTED FEB41975 SHEET l 0F 6 ROTARY HEAT ENGINE POWERED TWO FLUID COOLING ANDHEATING APPARATUS This application is a continuation-in-part of myapplication Ser. No. 316,851, filed Jan. 2, 1973 which is acontinuation-in-part of my earlier application Ser. No. 227,902, filedFeb. 22, l972, now abandoned.

This invention relates to rotary engine powered cooling and heatingapparatus, and more particularly to closed Rankine cycle engine poweredcooling and heating apparatus utilizing separate engine power fluid andrefrigerant fluid and having a condenser for the power and refrigerantfluids and an evaporator for the refrigerant fluid coupled to the enginefor rotation therewith as a unit.

An object of the present invention is to provide a rotary closed Rankinecycle engine powered cooling and heating apparatus that is of compact,unitary construction and both quiet and efficient in operation, andwhich is readily adapted to generate auxiliary electrical power.

Another object of the invention is to provide a rotary engine poweredcooling and heating apparatus having the features described that ishermetically sealed and does not require high speed seals for separatingportions of the apparatus operating with different power and refrigerantfluids at different pressures.

Another object of the invention is to provide a rotary engine poweredcooling and heating apparatus of the character set forth that isoperable to function either as a space cooler or heater as desired andthe rotary condenser and evaporator function also as blowers forcirculating the cooling or heating fluid independently of other powersources.

Still another object of the invention is to provide cooling and heatingapparatus as set forth employing a novel arrangement of capillaryexpander for the refrigerant fluid whereby the capacity balance of thesystem is automatically controlled.

A further object of the invention is to provide a cooling and heatingapparatus embodying the features set forth that can be manufactured andshipped fully assembled, hermetically sealed and charged with therefrigerant fluid and the power fluid.

These and other objects of the invention and the various features anddetails of the construction and operation thereof are hereinafter setforth and described with reference to the accompanying drawings, inwhich:

FIG. 1 is a typical sectional view diametrically through one embodimentof a rotary heat engine powered apparatus according to the presentinvention;

FIG. 2 is a transverse sectional view on line 2-2, FIG. 1;

FIG. 3 is an enlarged fragmentary vertical sectional view diametricallythrough the rotary heat engine;

FlG. 4 is a schematic view of the fixed-ratio gear train on line 44,FIG. 3;

FIG. 5 is an end elevational view in reduced scale of the torque anchorand pendulum shown in FIG. 3;

FIG. 6 is a view similar to FIGS. 1 and 3 showing another embodiment ofthe present invention;

FIG. 7 is a fragmentary view partially in section on lines 77, FIG. 6;

FIG. 8 is an end elevational view of the disclosure in FIG. 7;

FIG. 9 is a schematic diagram of an alternator circuit for theembodiment of the invention shown in FIG. 6;

FIG. 10 is a perspective view showing the apparatus of the presentinvention with associated duct work and valving arranged for cooling orair conditioning a building in the summertime or other warm temperatureclimate; and

FIG. I1 is a view similar to FlG. 10 showing the duct valving arrangedfor heating a building in the winter time or other cool temperatureclimate.

A two fluid rotary engine powered cooling and heating apparatusaccording to the present invention comprises a rotary closed Rankinecycle engine including a rotary housing H containing a power fluidboiler B, power fluid expander PX and a refrigerant compressor P. Acondenser C having separate portions C and C" for condensing the powerfluid and refrigerant fluid is mounted coaxially at one side of theengine housing, and a refrigerant evaporator E is coaxially mounted atthe opposite side of the engine housing. The power fluid expander PX isdriven at a predetermined speed by the pressure power fluid generated inthe boiler B and in turn drives the refrigerant compressor P. Thehousing-condenser-evaporator unit is rotationally driven at apredetermined lesser speed. Refrigerant condensed in the condenser isdelivered to the evapora tor through a capillary expander in which thecapacity balance of the expander is controlled and determinedautomatically by the pressure drop across the expander. The entirehousing unit is hermetically sealed and the closed Rankine cycle powerengine is adapted and designed for use with high molecular weight fluidsand different high molecular weight fluids may be employed for theboiler power fluid and for the refrigerant fluid.

Referring to the drawings, in the embodiment of the invention shown inFIGS. 1-4 of the drawings, and with reference particularly to FIG. 1thereof, the rotary engine housing H comprises a central generallycylindrical portion 1 and opposite end housing portions 2 and 3,respectively.

The central housing portion 1 includes an annular boiler compartment Band a lubricant sump compartment S, the latter being of slightly largerdiameter than the boiler compartment B and being axially spacedtherefrom by an intermediate cylindrical portion 4 of less diameter thanthe boiler B which has formed therein an annular vaporizing chamber 5that is heated by thermal conduction from the boiler B. The boilerchamber B is defined by an outer continuous circumferentially extendingwall 6, side walls 7 and 8 and an inner continuous wall 9. The sumpcompartment S is defined by an outer continuous circumferentiallyextending wall portion 10 and side walls 11 and 12, respectively.Preferably, the outer circumferential wall 6 of the boiler is providedwith circumferential fins 13, as shown, to increase the heat transferfrom the combustion gases and, alternatively, the boiler chamber wall 6may be configurated or contoured to provide an expander or extendedthermal conductive surface area in accordance with the inventiondisclosed in US. Pat. No. 3,690,302, issued Sept. 12, 1972. The outercircumferential wall 10 of the sump compartment S is also provided withcircumferential fins 14 to increase the heat transfer to the surroundingair from said wall 10 and thereby tend to cool lubricant in the sump S.

The engine housing H embodying the construction described is mounted forrotation about its axis by means of shafts l5 and 16 secured to andextending coaxially outward endwise from the housing end portions 2 and3, respectively. The outer end of the shaft is journalled by means of abearing 17 in a stationary hub 18 that is fixedly supported by means ofradial spokes 19 from a circumscribing concentric ring 20 that in turnis fixedly supported by a standard 21 from a fixed base or support 22 ofthe machine. In similar manner. the outer end of the shaft 16 isrotatably journalled by means ofa bearing 23 in a stationary hub 24 thatis supported by means of radial spokes 25 within a circumscribingconcentric ring 26 that in turn is fixedly supported by a standard 27from the fixed base 22 of the machine. From the foregoing, it will beapparent that the engine housing H including the central portion 1containing the annular boiler B and refrigerant sump S, together withthe end housing portions 2 and 3 and the shafts 15 and 16, constitute aunitary structure that is rotatably mounted by means of the bearings 17and 23 for coaxial rotation as a unit about the engine axis.

The rotary boiler is adapted to be driven about its axis at apredetermined speed of rotation calculated to create the centrifugalforce necessary to dispose and maintain the selected boiler power liquidtherein uniformly distributed circumferentially about and in contactwith the inner surface of the outer peripheral wall 6 of the boiler witha liquid/vapor interface, designated i in FIG. 1, that is highly stableand essentially cylindrical and concentric with the axis of rotation ofthe boiler. Essentially the liquid/vapor interface 1' is disposed at apredetermined radius from the rotation axis of the boiler to providehigh boiling heat fluxes in excess of those obtainable at ambientgravity.

Referring to FIGS. 1 and 2, the annular body ofliquid in the boiler maybe heated to the required boiling temperature to vaporize the same, forexample, by the combustion of a suitable fuel-air mixture in astationary combustion box 30 that circumscribes the rotatable boilerchamber B. Fuel for combustion is discharged into the combustion box 30from a nozzle 31 at the required rate and pressure, and air for mixturewith the fuel is discharged into the combustion box through a pluralityof ports 32 in the peripheral wall 33. A hood structure 34 defines aplenum chamber 35 into which the air is supplied through a duct 36 atthe pressure and volume required for efficient combustion of the fuel toheat the liquid in the boiler casing to the desired temperature. Theresidual combustion gases are discharged through an exhaust duct 37, anda stationary transverse baffle 38 configurated for complementaryinterfitting cooperation with the configuration of the boiler peripheralwall 6, is mounted intermediate the fuel nozzle 31 and exhaust duct 37to control recirculation of the combustion gases.

Coaxially mounted within the engine housing H for rotation with thelatter is an annular power fluid expander PX having a central bore 40extending coaxially therethrough as best shown in FIG. 3. The expanderPX is fixedly supported within the engine housing H by an annularsupport ring 41 that is in turn supported coaxially within the enginehousing by an integral radially extending partition portion 42 thatterminates at its outer periphery in an axially extending flange portion43 connected to the inner surface of the adjacent wall of the housingand forming therewith an annular collector ring 44 for the power fluidcondensate that is condensed in the condenser. The expander support ring41 and its radial partition portion 42 thus form with the adjacent endportion 3 of the housing H interiorly of the latter an engine powerfluid compartment X that is substantially closed from the remainder ofthe interior of the engine housing H. However, since there are nocontacting shaft seals some migration of fluid along the turbine shaftis possible and means, hereinafter described, are provided forseparating refrigerant fluid and power fluid in the event that admixturethereof should occur.

The power fluid expander PX is in the form of a single stage shroudedturbine comprising a rotor 45 having a series of turbine blades 46arranged peripherally thereabout. The turbine rotor 45 is fixedlymounted on a shaft 48 for coaxial rotation independently of the rotaryhousing-condenser-evaporator unit. The shaft 48 is rotatably mountedwithin the bore 40 of the expander PX. An annular series of nozzles 50is provided within the power fluid expander PX coaxially adjacent theturbine rotor 45 and in confronting relation to the blades 46 thereof.An annular high pressure manifold 51 is provided in the expander PX andopens to the turbine nozzles 50.

High pressure vapor is supplied from the boiler chamber B to themanifold 51 through a plurality of radial ports or passages 52 and acorresponding plurality of radially disposed vapor tubes 53 arranged inequally spaced relation circumferentially of the axis to insurerotational balance. Thus the high pressure vapor generated in the boilerchamber B passes from the latter through the tubes 53 and passages 52 tothe high pressure manifold 51 from which it is discharged through theturbine nozzles 50 and impinges upon the blades 46 to drive the turbinerotor 45 and its shaft 48 at the desired speed of rotation.

An annular diffuser 55 is provided in the ring 41 coaxially adjacent theturbine rotor 45 to receive the exhaust vapor from the expander, and theinlet opening thereto is disposed in confronting relation to the turbineblades 46 at opposite sides thereof from the nozzles 50. Exhaust vaporis discharged from the diffuser 55 into the engine power fluidcompartment X of the housing H from which it passes into the condenser Cas hereinafter described. A plurality of axially extending radialpartitions 56 are provided in the diffuser 55 and these, together withthe radial vanes 57 in the compartment X, function to maintain theangular velocity of the exhaust vapor the same as that of the rotatinghousing-condenser-evaporator unit.

Also mounted within the engine housing H coaxially adjacent the powerfluid expander PX is a refrigerant compressor or pump P. The compressorP comprises an annular housing structure 60 that is fixedly supportedwithin the engine housing H by means of an axially extending annularsupport sleeve 61 having integrally therewith a radially extendingcircumferential partition portion 62 that is connected at its peripheryto the internal surface of the central cylindrical portion 1 of thehousing H. The partition 62 is spaced axially from the partition 42 andsubdivides the remainder of the engine housing H, other than the fluidcompartment X, into a refrigerant compartment Y and an intermediatecompartment Z that is evacuated to provide thermal insulation betweenthe higher temperature power fluid compartment X and the lowertemperature refrigerant fluid compartment Y. By the constructiondescribed, it will be apparent that the compressor housing 60 rotatescoaxially as a unit with the rotary housing-condenserevaporator unit.

As shown in FIG. 3 of the drawings, the compressor housing structure 60defines interiorly thereof a coaxial annular chamber 64 having radialopenings 65 thereto from the refrigerant fluid compartment Y of thehousing H. Mounted in the chamber 64 of the pump P is a compressor rotor66 that is keyed to the engine shaft 48 to be driven thereby. Theturbine shaft 48 extends coaxially through the compressor housingstructure 60 and is journalled therein by bearings 68 and 69,respectively. Refrigerant vapor in the compartment Y of the housingentering the compressor or pump P through passages 65 is compressed bythe rotor 66 and then discharged through a plurality of radial passages70 to an annular manifold 71 and thence through a plurality of radialpassages 72 to an annular refrigerant manifold 73. The manifold 73circumscribes the compressor or pump P and is mounted to rotate with thelatter and the housing-condenser-evaporator unit by means of a pluralityof radial vanes 74 that are secured between the manifold 73 and adjacentsurface of the radial partition 62, for example by welding.

In the embodiment of the invention shown in FIGS. 1-3 of the drawings,the housing-condenser-evaporator unit is rotationally driven by amechanical coupling provided between the expander PX and the housing Hso that during operation of the engine, after start-up, the unit isrotationally driven continuously by the primary power output generatedby the engine. This is accomplished by means of an internal occludedfixedratio gear train arranged coaxially interiorly of the housing H,for example similar to that shown and described in the copendingapplication of Max F. Bechtold Ser. No. 206,779, filed Dec. 10, 1971,now US. Pat. 3,769,796.

As shown, the fixed-ratio gear train is in the form of a planetary gearsystem comprising a sun gear 76 fixedly mounted on and driven by theturbine shaft 48. The driven sun gear 76 drives a plurality of compoundplanet gears 77 each secured on a stub shaft 78 that is journalled bymeans of bearings 79 and 80 in an anchor plate member 81 and planet gearcarrier ring 82, respectively. Carrier ring 82 is rotationally mountedby means of bearings 83 and 84 on the coaxially extending hub portion60a of the compressor housing structure 60. As shown, the sun gear 76 ismeshed with and rotationally drives the larger diameter gear 77a of eachcompound planet gear 77, and the smaller diameter gear 77b of eachcompound gear is meshed with and drives a coaxial annular ring gear 86recessed within and carried by the compressor housing structure 60. Theanchor plate member 81 and the gear carrier ring 82 are connected to anon-rotating torque anchor member T having a coaxially disposed centralhub portion 87 that is journalled on the inner end of the engine housingshaft by means of bearings 88 and 89.

The torque anchor T includes an inner circumferential cup-shaped portion90 formed integral with the hub portion 87 and coaxially disposedadjacent the fixedratio gear train just described. The compound gearcarrier ring 82 is connected to the non-rotating torque anchor T by aplurality of circumferential equally spaced connector rods 91 eachhaving its inner end fixedly mounted in the carrier ring 82 and itsouter end portion extending through the anchor plate 81 and into analigned opening 93 in the cup portion 90 of the torque anchor T, each ofsaid connector rods 91 being secured in the anchor plate 81 by means ofa nut 94 threaded thereon. The torque anchor T is held stationary withrespect to the rotary housing-condenser-evaporator unit by means of apendulum element 95 that projects radially outward from the rim of thecup-shaped portion of the torque anchor T.

The pendulum 95 is of predetermined density. dimensions and location togenerate the desired counterforce to oppose the external reaction torqueof the air drag in the condenser and evaporator and, as a typicalexample, a pendulum element 95 made of steel in the configuration shownin H6. 5 of the drawings having an inner radius of 7.0 inches, an outerradius of l0.0 inches, a width of 0.75 inch, an arc length of andweighing 8.5 pounds, will provide a countertorque force sufficient tohold the torque anchor T stationary and prevent rotation thereof againsta reaction of 3.9 ft. lbs. which is the torque required to rotate theboiler-c0ndenser-evaporator unit at 2,400 rpm. when both the condenserand evaporator are pumping air.

By reason of the non-rotating torque anchor T the compound planetarygears are fixedly positioned so that their axes do not rotate or movecircumferentially relative to or about the engine axis. Thus, thebalance of the power output of the engine expander PX not used to drivethe compressor rotor 66 is transmitted from the driving sun gear 76through the compound planetary gears directly to the driven ring gear 86on the rotary boiler-condenser-evaporator unit thereby rotationallydriving said unit at the fixedspeed of the particular gear train.

As previously stated, exhaust vapor discharged from the turbine diffuser55 into the engine compartment X of the housing H enters the condenser Cwhere it is condensed, and, in accordance with the present invention,the compressed refrigerant discharged from the compressor P to themanifold 73 is also condensed in the condenser C.

The condenser construction shown comprises closely radially spaced outerand inner concentrically arranged annular condenser sections C and C"for the engine power fluid and the refrigerant fluid, respectively. Byproviding such concentric outer and inner condenser sections C and C athermal break or gap is provided between the two condenser sections sothat the outer power fluid condenser section can be operated at muchhigher temperatures for more efficient heat transfer than thesubstantially lower temperatures desired for efficient operation of theinner refrigerant condenser section.

Referring to the drawings, the outer and inner concentric condensersections C' and C" each comprises a coaxial array of closely spacedannular fins 96' and 96" fabricated of metal having high thermalconductivity as previously described, and disposed in radial alignmentwith respect to each other for efficient air flow therebetween. Heatexchange tubes 97 for the boiler power fluid extend longitudinallythrough the fins 96' of the outer condenser section C and heat exchangetubes 97" for the refrigerant fluid extend in similar mannerlongitudinally through the fins 96" of the inner condenser section C. Aspreviously described, the fins 96' and 96" consist of separate orindependent annular disk elements and are supported and secured inpredetermined equally spaced parallel relation with respect to oneanother by the heat exchange tubes 97' and 97",

respectively, the fins preferably being bonded to the heat exchangetubes to provide maximum thermal conductivity therebetween.

The inner end portions of the heat exchange tubes 97' of the outer powerfluid condenser section C extend through the adjacent wall of thehousing H and the tubes are in open communication with the condensatecollector ring 44 and at their outer ends are connected to a commonmanifold 99 formed in an annular outer end ring 100 that is supportedfrom the engine end housing portion 3 by a plurality ofcircumferentially equally spaced radial spokes 101. Power fluidcondensed in the heat exchange tubes 97' of the condenser collects inthe collector ring 44 and is returned through a plurality ofcircumferentially equally spaced radial tubes 102 to the boiler B wherethe power fluid condensate is again vaporized and the power cyclerepeated.

With respect to the refrigerant condenser tubes 97", all but apredetermined small number, for example three, of said tubes 97" areclosed at their inner ends by an annular plate 103 to which the innerends of said tubes are secured, and the outer ends of all of thecondenser tubes 97 are connected to a common manifold 104 also formed inthe condenser end ring 100. The predetermined small number of the heatexchange tubes 97 that are not closed at their inner ends by the annularplate 103 are of longer length than the remainder of the heat exchangetubes 97 and extend through openings 106 in the plate 103 and throughlarger openings 108 and 110 in the housing end portion 3 and radial wallportion 42 of the power fluid expander support ring 41, respectively, asmore clearly shown in FIG. 3 of the drawings, and are connected at theirinner ends to the annular refrigerant manifold 73 previously described.The openings 108 and 110, just mentioned, are larger in diameter thanthe refrigerant heat exchange tubes 97" extending therethrough in orderto accommodate insulating sleeves 112 of comparable diameter thatconcentrically circumscribe the portions of the heat exchange tubes 97"that pass through the power fluid compartment X in the engine housing H.The sleeves 112 are circumferentially spaced from the heat exchangetubes 97" and function to insulate the cooler refrigerant in theenclosed portions of the tubes 97" from the surrounding high temperaturepower fluid in the housing compartment X.

Liquid refrigerant condensed in the heat exchange tubes 97" flowsoutwardly endwise therein to the manifold 104 in the end ring 100 andthence inwardly through the aforesaid small number of said tubes to theannular refrigerant manifold 73 from which it is conducted by a smallnumber of circumferentially arranged equally spaced capillary expandertubes 114 which deliver the low temperature mixture of refrigerantliquid and vapor to an annular inlet manifold ring 116 of the evaporatorE. As shown in FIG. 3, a portion of each of the capillary expander tubes114 passes through the vaporizing chamber of the central portion 1 ofthe engine housing H and is thermally insulated therefrom by a spacedcircumscribing sleeve 118. Each capillary tube then extends radially toa point adjacent the periphery of the lubricant sump portion of thehousing and thence axially through the peripheral wall of the latter andthence radially inward and into the refrigerant compartment Y of thehousing with its end terminating in the evaporator inlet manifold 116.

The evaporator E comprises a coaxial array of closely spaced annularradial fins 120 and a plurality of heat exchange tubes 122 extendinglongitudinally through said fins arranged circumferentially in equallyspaced relation about the engine shaft 15. The inner ends of theevaporator heat exchange tubes 122 extend through the radial wallportion of the housing end portion 2 and are connected to therefrigerant inlet manifold 116 as shown. The outer ends of the tubes 122are mounted in recesses in an annular end ring 124 and connected to anannular manifold 126 provided therein. The end ring 124 is disposedcoaxially adjacent the outermost of the evaporator fins 120 andsupported from the engine housing end portion 2 by a plurality ofcircumferentially arranged equally spaced spokes 128. By theconstruction described, the evaporator E is fixedly mounted with respectto the engine housing H for rotation therewith and with the condenser Cas a unit. The low temperature refrigerant delivered to the manifold 116enters the evaporated heat exchange tubes 122 where it is evaporated andreturned to the refrigerant manifold 116. The evaporator inlet mani fold116 is in open communication inwardly thereof with the interior of thehousng refrigerant compartment Y and hence evaporated refrigerantreturned from the tubes 122 to the manifold 116 is delivered to thecompartment Y of the engine housing and thence to the compressor P whereit is again compressed to repeat the refrigerant cycle.

A feature of the invention resides in the construction and arrangementof the capillary expanders 114 and the evaporator E whereby therefrigerant flow rate in the capillary expander tubes 114 isautomatically adjusted according to the refrigerant flow rate throughthe compressor P to thereby maintain the capacity balance of therefrigerant system. In this connection, it is desirable that the radialdistance of the liquid level in the evaporator tubes 122 from the engineaxis be greater than the radial distance of the refrigerant condensertubes 97" from the engine axis so that the flow rate of refrigerantthrough the capillary expander tubes 114 is controlled by the pressuredrop across the capillary expander tubes 114. This pressure drop isdeter mined not only by the difference between the pressure of the vaporat the refrigerant manifold 73 and that of the vapor at the evaporatorinlet manifold 116, but also by the difference in liquid level betweenthe level r in the radially extending inlet portions of the expandertubes 114 adjacent the refrigerant manifold 73 and the level in theevaporator tubes 122.

Thus, when the compressor P delivers refrigerant at a high flow rate,the liquid lever r in the expander tubes 114 will move radially inwardtherein to provide the additional pressure necessary to drive therefrigerant through the capillary expander tubes 114 at the propermatching flow rate in relation to the delivery flow rate of thecompressor P. Due to the amplifying effect of the centrifugal forcecreated by rotation of the housing-condenser-evaporator unit, smallvariations in the liquid level r will compensate for wide variations inthe flow rate of the refrigerant and the described arrangement ofcapillary expander and evaporator is 0perable to provide a capacitybalanced system for any refrigerant flow rate from the designed flowrate of the particular apparatus to zero flow of the refrigerant,

The annular fins of the condenser C and evaporator E define interiorlythereof coaxial inlet chambers 130 and 132, respectively, for a coolingfluid to be discharged outwardly by and between the rotating tins of thecondenser and evaporator as hereinafter set forth. The inner diametersof the outer condenser end ring 100 and adjacent engine support ring 26and the outer end ring 124 of the evaporator and the adjacent enginesupport ring 20 are the same as the inner diameters of the condenserfins 96" and evaporator fins 12, respectively, so as not to restrict theflow of fluid inwardly of the chambers 130 and 132. Outwardly flared orbellshaped fluid intake members 134 and 136 are fixedly mounted on theengine support rings 26 and 20, respectively, in coaxial relationoutwardly adjacent the inlet ends of the chambers 130 and 132.

The axial spacing between the adjacent annular fins 96' and 96" of thecondenser sections C and C" and the relationship of the inner radius ofthe inner fins 96' to the outer radius of the outer fins 96' may varybetween predetermined ranges or limits for any given range of speeds ofrotation (r.p.m.) of the condenser, and are determined so as to utilizethe viscous properties of the condenser cooling fluid and evaporatorheat exchange fluid and the shear forces exerted thereon by the rotatingfins to convey and accelerate the fluid radially outward between thefins of the condenser C and the evaporator E substantially to thevelocity providing optimum total heat exchange between the fluids in theheat exchange tubes and the fluid passing outwardly between said fins.

The nature of the flow for rotational shear force devices is completelydescribed by the Taylor number, N where:

d distance between fins w angular velocity (radians per sec.)

v kinematic viscosity We have found that most efficient pumping occurswhen N 3.25. However, efficient fluid pumping does not lead to anefficient heat exchanger. Efficient pumping occurs when the energytransfer to the fluid is maximized. Efflcient heat exchange depends uponboth the fin area and the difference between the speed of the tins andthe velocity of the fluid flowing between them. Thus, for heat transfer,the Taylor number is not adequate by itself to completely describe anoptimum configuration. We have found that for various combinations ofinner radius (Ri) of the inner fins 96'' and the outer radius (R) of theouter fins 96' the Taylor number for efficient heat exchanger willalways be greater than 4.5. The precise values of Taylor number and theratio of the inner to outer radii of the fins depend upon thethermodynamic and transport properties of the fluids exchanging heat andwhether the heat transfer mechanism for the fluid in the heat exchangetubes is boiling, condensing or convective.

For heat transfer to or from air on the fin side to or from a boiling orcondensing fluid within the tubes, it has been determined that theTaylor number for an efficient heat exchanger is within the range offrom 5.0 to 10.0 and the inner to outer radii ratio of the fins iswithin the range of from 0.70 to 0.85. For optimum results the Taylornumber will be in the neighborhood of about 6.0 and the tin radii ratiowill be in the neighborhood of about 0.77, and these values constitutegood starting points for the design of an efficient heat exchangeraccording to the present invention. The particular optimum design andoperating conditions for any given heat exchanger for installation canbe determined by a person skilled in the art. It has been determinedthat the values of Taylor number and fin radii ratio for other gaseousfluids are essentially the same as the values stated for air.

The axial spacing between the fins of the evaporator E and the inner andouter radii ratio thereof is similarly determined with relation to therotational speed of the unit and kinematic vicosity ofthe evaporatorheat exchange fluid, such as air. to provide a Taylor number and finradii ratio the same as previously described for the condenser C.

The location radially of the split or division between the fins 96' and96" of the outer and inner condenser sections C and C is also importantand depends upon a number of factors such as the power and refrigerantfluids employed, their thermodynamic cycles and heat transfercoefficients, the heat transfer properties of the particular materialsof which the condenser fins and heat exchange tubes are fabricated, andmust be determined for each case. The follow equation provides a gooddesign starting point:

2 12 '1 iii/ r (11 2 o) Where A inner section fln area A outer sectionfin area q, inner section heat transfer rate outer section heat transferrate t temperature of the air entering the condenser t saturationtemperature of the refrigerant fluid in the inner section of thecondenser t saturation temperature of the power fluid in the outersection of the condenser Incorporated in the apparatus is a forced-feedlubrication system utilizing a Pitot pump of the type described andclaimed in my copending application Ser. No. 231,232, filed Mar. 2,I972, now U.S. Pat. No. 3,744,246. As shown, the Pitot pump comprises atube that extends radially outward through the pendulum 95 and has atits outer end an L-shaped scoop portion 141, the inlet end of which isimmersed in an annular bath of lubricant 142 extending circumferentiallyinteriorly of the lubricant sump portion S of the engine housing H andfacing in the direction opposite the direction of rotation thereof. Fromthe pendulum 95 the tube 140 extends inwardly and has its inner endextending into the torque anchor hub portion 87 and connected to theaxially extending lubricant passage 144 provided therein. From passage144 lubricant is conducted through an S-shaped tube section 146 to alubricant passage 148 formed coaxially in the turbine shaft 48 andhaving radial ports 149a, 150 communicating with the turbine shaftbearings 69 and 68 to supply lubricant thereto. Lubricant supplied tothe bearing 68 drains through a passage 152 and returns to the lubricantbath 142 in the sump S, and lubricant supplied to the shaft bearing 69drains in part back through radial port 149 to bearing 84. Lubricantoverflow from hearing 84 and from bearing 69 drains back through thefixed-ratio gear train and similarly is returned to the lubricant bath142 from which the lubricant is recirculated by the Pitot pump by reasonof the rotation of the engine housing l-l relative to the non-rotatingtorque anchor T and its pendulum portion 95.

Any refrigerant vapor and other non-condensable gases that may migrateinto the power fluid system of the engine will flow through thecondenser tubes 97 and collect in the manifold 99 from which they arereturned through a plurality of circumferentially equally spacedlongitudinally extending tubes 154 to the refrigerant compartment Y ofthe engine. Similarly, since the volatility of the power fluid is muchless than that of the refrigerant, any power fluid which may migrateinto the refrigerant system will collect in the evaporator manifold 126at the outer end of the heat exchange tubes I22 and overflow, as a powerfluid rich mixture, into a plurality of circumferentially equally spacedradial weir tubes 156 and thence through a corresponding plurality oflongitudinally extending tubes 158 to the refrigerant compartment Y ofthe engine. The migratory power fluid mixes with the lubricant in bath142 while the liquid refrigerant tends to vaporize due to the elevatedtemperature of the bath 142 as compared to the evaporator. Migratorypower fluid that collects in the lubricant bath 142 in the sump S raisesthe lubricant liquid level of the bath 142 and the excess powerfluidlubricant mixture is removed therefrom by a radial tube 160 mountedin the pendulum 95 and having at its outer end an L-shaped scoop portionthe inlet end of which faces opposite the direction of rotation of theengine housing H and disposed at the surface level of the lubricant bath142. Power fluid-lubricant mixture picked up by the tube 160 isdischarged from the inner end of said tube into an annular collectorring 163 from which it is conducted by a tube 164 to the annularvaporizing chamber previously described, wherein the power fluid isvaporized and returned by a plurality of circumferentially equallyspaced tubes 166 to the power fluid compartment X of the housing H. Thelubricant residue is not vaporized in chamber 5 and drains therefrom andis returned by a tube 168 to the lubricant bath 142 in the sump S.

In operation of the embodiment of the engine shown in FIGS. 1-5 of thedrawings, it will be apparent at start-up that there will be no pressurevapor generated by the boiler B to drive the expander PX and in turn thehousing-condenser-evaporator unit. Consequently, at start-up it isnecessary to independently drive the housing-condenser-evaporator unitat the designed predetermined speed of rotation to establish andmaintain the liquid/vapor interface i in the boiler chamber until theannular body of the power fluid liquid therein is heated to thetemperature required to produce the desired pressure vapor to drive theengine rotor 45 and its shaft 48. This may be accomplished, for example,by means of a starter motor M driving a pulley 170 fixed on theevaporator end ring 124 through a belt 172. Means such as a clutch (notshown) can be provided for breaking the drive between motor M and pulley170 when the engine attains normal operation, or the motor M cancontinue to be driven by the rotating housing-condenser-evaporator unitto function as a generator operable, for example, to provide electricpower for external equipment and accessories such as batteries for thestarter motor M, lights and the like.

In normal operation of the rotary engine shown in FIGS. 1-5 of thedrawings, with the annular body of liquid in the boiler chamber heatedto the required temperature and pressure by combustion of fuel-airmixture in the chamber 30, the pressure generated in the boiler isdischarged inwardly through tubes 53 to the manifold 51 and thencethrough nozzles 50 into impinging contact against the turbine blades 46thereby driving the engine rotor 45, shaft 48, compressor rotor 66 andthe sun gear 76 at the desired predetermined speed of rotation. Thesun-gear 76 through the fixedratio gear train previously describeddrives the rotary housing-condenser-evaporator unit at a predeterminedsubstantially slower speed of rotation relative to the shaft 48determined by the fixed-ratio of the gear train. In the embodiment ofthe invention shown in FIGS. l-S of the drawings, the direction ofrotation of the housing-condenser-evaporator unit is opposite thedirection of rotation of the turbine rotor 45 and shaft 48.

The exhaust vapor from the power fluid turbine discharges through thediffuser 55 into the-compartment X of the engine housing and enters theheat exchange tubes 97' of the outer condenser section C where it iscondensed by the cooling fluid discharged outwardly between the fins96', as previously described. The power fluid condensate flows inwardlyin the tubes 97' to the collector ring 43 from which it is returnedthrough tubes 102 to the boiler B at a controlled rate equal to the rateof vaporization of the power fluid in the boiler.

Refrigerant fluid in the housing compartment Y enters the compressor Pthrough inlet passages 65, is compressed by the rotor 66 and dischargedthrough diffuser passages 70, manifold 71 and passages 72 to the annularrefrigerant manifold 73. From the manifold 73 the compressed refrigerantis delivered to the inner refrigerant condenser section C" through thesmall number of the heat exchange tubes 97" that is connected to saidmanifold 73 and is distributed by the manifold 104 into all of therefrigerant condenser heat exchange tubes 97" where it is condensed bythe cooling fluid discharged outwardly between the fins 96", aspreviously described. The condensed refrigerant is returned to therefrigerant manifold 73 through the small number of heat exchange tubes97" connected thereto and is delivered through the capillary expander114 to the .evaporator inlet manifold 116 and thence into the evaporatorheat exchange tubes 122 wherein it is evaporated by heat exchange withthe fluid discharged outwardly between the evaporator fins 120, aspreviously described. Refrigerant fluid vaporized in the evaporatortubes 122 flows inwardly therein to the manifold 116 and thence into therefrigerant compartment Y of the engine housing to be again compressed,condensed and evaporated, as previously described.

A typical example of closed Rankine cycle rotary engine powered heatingand cooling apparatus embodying the construction shown in FIGS. 1-5 anddesigned for an output of 8.77 hp at the turbine shaft 48, comprises aboiler B having a liquid level 1' diameter of 9.0 inches and an axialinternal length sufficient to provide the heat input required to theboiler liquid from the combustion gases. The diameter of the boilerexpander turbine at the blades 46 is of the order of 3.1 inches and thediameter of the compressor is of the order of 3.5 inches. The fins 96 ofthe outer power fluid condenser C have an outer diameter of 13.1 inchesand an inner diameter of 12.1 inches. The fins 96" of the innerrefrigerant condenser C have an outer diameter of 12.0 inches and aninner diameter of 10.0 inches. The axial length of the series ofcondenser fins 96' and 96 is l0.0 inches and the spacing betweenadjacent fins is 0.028 inches with the axes of the heat exchange tubesdisposed at a radius from the rotation axis of the apparatus of 5.5inches for the inner condenser section C" and 6.3 inches for the outercondenser section C. The fins 120 of the evaporator E have an outerdiameter of 14.0 inches and an inner diameter of 11.0 inches. The axiallength of the series of evaporator fins is 5.6 inches and the spacingbetween adjacent fins is 0.025 inches. The axially extending evaporatortubes 122 are also disposed at a radius of 6.25 inches from therotational axis of the apparatus. The housing-condenserevaporatorassembly is rotationally driven at a speed of 2,400 rpm. by the turbinethrough fixed-ratio gear train in the direction opposite to rotation ofthe turbine rotor 45. Using as the boiler power fluid a mixture oftrichlorodifluorobenzene isomers, as disclosed in patent applicationSer. No. 172,513, filed Aug. 17, 1971 by Max F. Bechtold and Charles W.Tullock, now Patent No. 3,774,393 and1,1,2-trichloro-1,2,2-trifluoroethane as the refrigerant fluid, thespecifications of a typical operation of the designed apparatus are asfollows:

Evaporator pressure (psia) 2 7 Evaporator load (Btu/hr) 24,000:Evaporator air flow (cfm) 800. Available surplus power (watts) 850.

In the foregoing example the power fluid condenser pressure (4.0 psia)is somewhat higher than the evaporator pressure (2.7 psia), and this isnecessary when power for a generator is to be supplied in addition toair-conditioning or heating. The higher full power condenser pressureinsures sufflcient turbine nozzle expansion ratio in spite of the powervariations which occur with varying generator load. Such an arrangementinsures that the refrigerant vapor in the end of the power fluidcondenser does not decrease the capacity of the power fluid condenser.

The present invenion is not limited to use of an internal gear train aspreviously described to rotationally drive thehousing-condenser-evaporator unit directly from the internal power fluidexpander, and in many installations it may be advantageous torotationally drive the housing-condenser-evaporator unit continuously bymeans of an electric motor mounted externally of the unit and suppliedwith electric current generated by an alternator mounted internally ofthe rotary engine housing coaxially thereof and driven by the internalpower fluid expander. In addition to supplying electric power to theunit drive motor, the alternator may also supply electric power forappliances, lighting and other electrical equipment.

One embodiment of such an arrangement is shown in FIGS. 6, 7, 8 and 9 ofthe drawings and, except for the differences hereinafter set forth, isgenerally similar in construction and operation to the embodiments ofthe invention previously described. Referring to FIG. 6 of the drawings,the rotary boiler B is formed integral within the coaxial engine housingH. The engine housing H comprises a central cylindrical portion 1 andaxially spaced end housing portions 2 and 3 at respectively oppositesides thereof. The engine housing H and boiler B are mounted forrotation about their common axis by means of shaft members 15 and 16extending coaxially outward from the opposite housing portions 2 and 3,respectively. The outer end of the shafts 15 is journalled by means of abearing 17' in a stationary hub 18 fixedly supported by means of radialspokes 19 from a circumscribing concentric ring 20 that is fixedlysupported from a fixed base or support (not shown) of the machine in amanner similar to that shown in FIG. 1. In similar manner the outer endof the other shaft 16' is rotatably journalled by means of a bearing(not shown) mounted in a stationary hub 24 that is supported by means ofradial spokes 25 within a circumscribing concentric ring 26 that is inturn fixedly supported from the fixed base of the machine. From theforegoing it will be apparent that the cylindrical boiler B and enginehousing H together with the aforesaid shafts l5 and 16 constitute aunitary structure that is rotatably mounted for coaxial rotation as aunit about the engine axis.

As in the embodiment previously described, the rotary boiler B isadapted to be driven about its axis at a predetermined speed of rotationcalculated to create the centrifugal force necessary to dispose andmaintain the selected boiler liquid therein uniformly distributedcircumferentially about and in contact with the inner surface of theouter peripheral wall of the boiler with a liquid/vapor interface,designated i. The annular body of liquid in the boiler may be heated tothe required boiling temperature by combustion of a suitable fuel-airmixture in a stationary combustion box 30' constructed and arranged aspreviously described and shown in FIG. 2 of the drawings.

Coaxially mounted within the engine housing H for rotation with thelatter is an annular power fluid expander PX having a central bore 40extending coaxially therethrough. The expander PX is fixed supportedcoaxially within the rotatable engine housing H by means of annnularring 41 having a radially extending circumferential wall portion 42 thatterminates at its periphery in an annular collector ring 43. The ring 43is in sealing engagement with the internal wall surface of the housingend portion 3 and forms therewith a closed power fluid compartment Xwithin the engine housing H so that the power fluid is effectivelysegregated from the refrigerant fluid and there is no substantialintermixing thereof.

The expander PX shown is in the form of a single stage shrouded turbinecomprising a rotor 45 having a series of turbine blades 46 arrangedperipherally thereabout. The turbine rotor 45 is keyed on a shaft 48 forcoaxial rotation therewith independently of the boiler B and enginehousing H. The shaft 48 is rotatably mounted in the bore 40 of theexpander PX by means of a bearing mounted in an annular internal housing182 having a coaxially extending cylindrical casing portion 184 for analternator A hereinafter described. The housing member 182 is mounted inthe rotary housing H for rotation therewith by means of an annularsupport ring 186 having an angularly extending circumferential webportion 188 that terminates in an annular refrigerant manifold 190. Thesupport ring 186 is secured coaxially within the engine housing H bymeans of struts 192 and 194 secured at opposite sides of the web portionof the ring for example, by welding.

An annular series of nozzles 50 is provided in the expander PX inconfronting relation to the blades 46 of the turbine rotor 45 and anannular manifold 51 opens to the turbine nozzles 50. High pressure vaporis supplied from the boiler B to the manifold 51 through a plurality ofradial passages 52 in the expander and a corresponding plurality ofradially disposed vapor tubes 53 arranged in equally spaced relationcircumferentially of the engine axis to insure rotational balance. Thus,high pressure vapor supplied to manifold 51 is discharged through theturbine nozzles 50 and impinges upon the blades 46 to drive the turbinerotor 45 and its shaft 48 at the desired speed of rotation.

An annular diffuser 55 mounted coaxially within the expander supportring 41 receives the exhaust vapor from the turbine and discharges saidvapor into the power fluid compartment X of the engine housing H fromwhich it passes into the condenser C which, in the illustratedembodiment is constructed and operable substantially as previouslydescribed and shown in FIGS. 1-3 of the drawings. A plurality of radialpartitions 56 and vanes 57' is provided to maintain the angular velocityof the exhaust power fluid vapor the same as that of the rotatinghousing unit H. Power fluid vapor condensed in the condenser collects inthe collector ring 43 and is returned through a plurality ofcircumferentially equally spaced radial tubes 102 to the boiler B wherethe condensate is again vaporized and the power cycle repeated.

As shown, the turbine shaft 48 extends coaxially an appreciable lengthoutwardly from the turbine rotor 45 and has its outer end portionrotatably supported in a bearing 196 mounted in the annular housing 198of a compressor or pump P disposed coaxially of the turbine shaft 48.The peripheral surface of the compressor housing 198 is in sealingengagement with a shoulder 200 provided interiorly of the engine housingportion 2 and forms with the latter an enclosed refrigerant compartmentY in the engine housing H. Between the power fluid compartment X andrefrigerant compartment Y, the housing H defines internally thereof asealed intermediate compartment Z which is evacuated to thermallyseparate the two compartments X and Y from each other and minimize heatexchange between the high temperature power fluid and the substantiallylower temperature refrigerant fluid.

In the embodiment illustrated, the alternator A is of the known inductoralternator type, such as Rice, Lundell or homopolar. The alternator isenclosed within a casing 202 mounted coaxially of the engine within thecylindrical casing portion 184 of the housing member 182 and thealternator armature 204 is integral with the turbine shaft 48' androtationally driven by the turbine rotor 45. The alternator fieldwindings 206, 2060 and 235 and the alternator casing 202 are fixedlysecured to the housing 182 and the outwardly adjacent compressor housing198 so that the latter as well as the armature casing and field windingsrotate as a unit with the engine housing H and relative to thealternator armature 204 driven by the turbine rotor 45.

The compressor housing 198 has an internal coaxial rotor chamber 208therein having a coaxial inlet 210 thereto that is in open communicationwith the interior of the refrigerant compartment Y. A compressor rotor212 is rotatably mounted in the compressor housing 198 and keyed to theturbine shaft 48 to be rotationally driven thereby. By this constructionvaporized refrigerant in the compartment Y enters the compressor housing198 through the inlet 210 and is compressed by the rotor 212 from whichit is discharged through a plurality of radial diffuser-passages 214formed in the housing 198 to an annular manifold 216 therein. From themanifold 216 the compressed refrigerant flows through a plurality ofcircumferentially equally spaced passages 218 to the annular refrigerantmanifold 190 and thence into the condenser C where it is condensed.

As previously stated the condenser is constructed as previouslydescribed and shown in FIGS. 1-3 of the drawings, and comprisesconcentric outer power fluid and inner refrigerant fluid condensersections C and C" each comprising a coaxial array of spaced annular fins96 and 96" having a plurality of heat exchange tubes 97 and 97",respectively, extending longitudinally therethrough and arranged inequally spaced relation circumferentially about the engine axis, aspreviously described. The heat exchange tubes 97 of the outer powerfluid condenser section C are connected at their inner ends to thecollector ring 44 and at their outer ends are connected to a commonmanifold 99 formed in an annular end ring 100 that is supported from theengine housing portion 3' by a plurality of circumferentially equallyspaced radial spokes 101.

As in the previous embodiment, all but a predetermined small number ofthe refrigerant condenser tubes 97" are closed at their inner ends by anannular plate 103 to which the inner ends of the tubes are secured, andthe outer ends of all of the refrigerant condenser tubes 97" areconnected to a common manifold 104 also formed in the condenser and ring100. The predetermined small number of the heat exchange tubes 97 thatare not closed at their inner end portions extend through openings 106in the plate 103' and through larger openings 108 and 110 in the enginehousing portion 3 and wall portion 42 of the ring 41, respectively, andare connected at their inner ends to the refrigerant manifold 190previously described. The openings 108 and 110' are larger in diameterthan the refrigerant heat exchange tubes 97 extending therethrough inorder to accommodate insulating sleeves 112 of comparable diameter thatconcentrically circumscribe the portions of the heat exchange tubes 97that pass within the power fluid compartment X. The sleeves 112 arecircumferentially spaced from the heat exchange tubes 97" and functionto insulate the refrigerant in the enclosed portions of the tubes 97"from the high temperature power fluid in the compartment X of thehousing H.

As in the previous embodiment, liquid refrigerant condensed in the heatexchange tubes 97" flows outwardly therein to the manifold 104 in endring 100 and thence inwardly through the predetermined small number ofsaid tubes to the refrigerant manifold 190 from which it is conducted bya small number of circumferentially arranged equally spaced capillaryexpander tubes 114 that deliver the low temperature mixture ofrefrigerant liquid and vapor to an annular inlet manifold 116 of theevaporator E.

The evaporator E, constructed and operable substantially as previouslydescribed and shown, comprises a coaxial array of annular radial fins120 and longitudinally extending heat exchange tubes 122circumferentially arranged in equally spaced relation about the engineshaft 15 and mounted for rotation with the engine erant inlet manifold116 as shown. The outer ends of the tubes [22' are mounted in recessesin an annular end ring I24 and connected to an annular outlet manifoldl26 provided therein. The end ring 124 is disposed coaxially adjacentthe outermost of the fins 120 and supported from the end housing portion2' by a plurality of circumferentially arranged equally spaced tubes220. The outer ends of the tubes 220 are connected to the annularmanifold I26 and the inner ends of said tubes 220 are connected to theinterior of the refrigeration compartment Y of the engine housing H. Thelow temperature refrigerant delivered to the manifold 126' enters theevaporator heat exchange tubes 122 where it is evaporated. Theevaporated refrigerant collects in the manifold 126 and is returnedthrough the tubes 220 to the refrigerant compartment Y and thecompressor P to repeat the cycle.

As previously stated, the housing-condenserevaporator unit is rotatablydriven at a predetermined constant speed of rotation, and in theillustrated embodiment of the invention, this is accomplished by meansof an external constant speed motor M driving a pulley 170 secured onthe evaporator end ring 124, through a belt 172.

The spacing between the adjacent annular fins 96 and 96" of thecondenser sections C and C and the spacing of the evaporaton fins 120 isdetermined with relation to the rotational speed at which thehousing-condenser-evaporator unit is driven and to the kinematicviscosity of the cooling fluid, such as air, to provide a Taylor numberin the range of about 5 to 10, preferably about 6, and the outer radiusof the fins 97 and the inner radius of the fins 97" are determined toprovide a ratio of inner to outer radii of the fins in the range of 0.70to 0.85, preferably about 0.77, as previously described, whereby theviscous properties of the fluid and the shear forces exerted thereon bythe rotating fins are utilized as previously described to convey andaccelerate the fluid radially outward between said fins substantially tothe velocity providing optimum total heat exchange between the fluids inthe heat exchange tubes and the fluid passing outwardly between thefins.

Any refrigerant vapor and other non-condensable gases that may migrateinto the power fluid system of the engine will flow through thecondenser tubes 97 and collect in the manifold 99 from which they arereturned through a pair of diametrically arranged tubes 154' to theinlet manifold 116 of the refrigerant evaporator E. Similarly, since thevolatility of the power fluid is much less than that of the refrigerant,any power fluid which may migrate into the refrigerant system willcollect in the evaporator outlet manifold 126 and overflow into a pairof diametrically arranged radial weir tubes 156 and thence through acorresponding pair of longitudinally extending tubes 158 to an annularvaporizing chamber 5 provided inwardly adjacent the boiler B and heatedthereby. Power fluid liquid returned to the chamber 5 is vaporizedtherein and passes inwardly through a plurality of equally spaced radialtubes 166 to the collector ring 44 and power fluid compartment X of theengine. Each of the tubes I58 extends l80 circumferentially about thehousing H and a liquid trap 222 is provided in each tube 158 to preventthe refrigerant from flooding into the power fluid condenser on shutdown of the engine.

In the embodiment of the invention illustrated in FIG. 6, provision ismade for cooling the alternator A by the circulation of ambient air incontact with the outer cylindrical wall surface of the alternator casing202. As shown in FIGS. 6, 7 and 8 of the drawings. a plurality ofcircumferentially equally spaced U-shapcd groove passages 224 is formedin the internal surface of the casing portion I84 of the alternatorhousing 182. The passages 224 are open to the external surface of thealternator casing 202 so that air flowing through said passages 224 isin contact with the outer surface of the alternator casing thus coolingthe alternator A.

Cooling air enters the passages 224 through a corresponding plurality ofaxially extending inlet tubes 226 that are open to the condenser airinlet chamber and the portions of said tubes 226 that pass through thepower fluid compartment X of the engine are shielded from the hightemperature therein by means of sleeves 228 that circumscribe the saidtubes in spaced relation thereto. Cooling air is exhausted from thepassages 224 through radially extending outlet tubes 230 having theirouter ends opening to the ambient atmosphere exteriorly of the rotaryengine. The discharge ends of the outlet tubes 230 are radially spacedfrom the engine rotation axis a distance sufficiently greater than theopenings to the inlet tubes 226 so that rotation of the engine causes apumping action that operates to draw ambient air inwardly of the tubes226, through passages 224 and discharge same outwardly through the tubes230.

The alternator A generates alternating current which is conducted fromthe engine housing H through a conventional slip-ring arrangementcomprising a plurality of rotating contacts 232 carried by the outer endportion of the engine shaft 15 and having electrical contact with thecorresponding number of circumscribing ring contacts 234 fixedly mountedin the stationary hub 18 of the engine as shown in HO. 6. A typicalalternator electrical circuit is illustrated schematically in FIG. 9 ofthe drawings.

Referring to FIG. 9 of the drawings, three phase alternating currentgenerated by the alternator A is conducted from the alternator statorwindings 235 through conductors 236 to three of the rotating contacts232 and thence through the corresponding stationary ring contacts 234and conductors 238 to a transformer 240. Conductors 242 conduct thecurrent from the transformer 240 to a rectifier 244 which converts thealternating current generated by the alternator A to direct current. Thedirect current from the rectifier 244 is conducted by a pair ofconductors 246 to the line conductors 248 of a service circuit thatincludes the main load terminals 250, the engine drive motor M and astorage battery 252 for the latter. The input terminals of a voltageregulator 254 are connected by a pair of conductors 256 to the aforesaidconductors 246 and the output terminals of the regulator 254 areconnected by conductors 258 to the remaining two ring terminals 234whereby current for field coils 206 and 206a for armature magnetizationis supplied through the corresponding rotary contacts 232 and conductors260.

In operation of the engine, it will be apparent at startup that therewill be no pressure vapor generated by the boiler B to drive theexpander PX, alternator A and refrigerant compressor P, andconsequently, the rotary housing-condenser-evaporator unit isrotationally driven at the designed predetermined speed of rotation bythe external motor M energized solely by the battery 252 until theliquid in the boiler is heated and produces the required power fluidpressure vapor to drive the alternator A, and generate the electricalcurrent required for operation of the electrical system as described.

A typical example of closed Rankine cycle rotary cngine powered heatingand cooling apparatus embodying the construction shown in FIGS. 6-9 ofthe drawings and designed for an output of 8.77 hp at the turbine shaft48 with 1.34 hp available for driving motor generator M to produceelectrical power, comprises a boiler B having a liquid level 1" diameterof 9.0 inches and an axial internal length of 4.2 inches to provide theheat input from the combustion box 30 required to the boiler liquid. Theremaining dimensional data for the embodiment of the apparatus shown insaid FIGS. 6-9 and the specifications of a typical operation thereof arethe same as previously set forth for the embodiment of the apparatusshown in FIGS. 1-5 of the drawings, except that the surplus poweravailable at the load terminals 250 is 750 watts.

Apparatus embodying the present invention is wellsuited for cooling orheating the interior of buildings, homes and other enclosed structures,and typical arrangements thereof for summer and winter operations areshown in FIGS. 10 and 11, respectively, of the drawings.

Referring to FIGS. 10 and 11, apparatus embodying the invention is shownwith associated ducts and valves arranged for cooling and heating abuilding, respectively. Preferably, the apparatus is located adjacent awall or walls of the building for convenient access to the atmosphereoutside the building such as, for example, adjacent the corner of twoside walls 264 and 266 of a building, as shown.

In the arrangement shown, air from outside the building is supplied tothe inlet of the rotary condenser C of the apparatus through ahorizontal duct 268 that extends inwardly through the building wall 264and connects at its inner end to an inlet housing 270 having an opening272 to the condenser inlet. The outer end of the duct 268 is providedwith suitable valve closure means such as shutters 274 which may beopened, as shown, to admit outside air through the duct to thecondenser, or closed to prevent the admission of outside air to thecondenser.

A stationary housing or plenum chamber 276 circumferentially enclosesthe rotary condenser C of the apparatus and air admitted to thecondenser C is discharged outwardly through the condenser flns 96' and96" where it is heated by heat exchange with the hot power fluid beingcondensed in the condenser tubes 97. An exhaust duct 278 for the heatedair discharged into the plenum chamber 276 leads tangentially therefromand then outwardly through the building wall 266 to the exterior of thebuilding. The outlet end of the duct 278 is also provided with suitablevalve closure means, such as shutters 280, for opening or closing theduct inlet to the outside atmosphere. A distribution duct 282, forconveying heated or cooled air from the apparatus to suitable outlets284 appropriately located throughout the building, has an inlet theretoconnected at 286 to the exhaust duct 278.

Similar to the condenser plenum chamber 276, the rotary evaporator isalso circumferentially enclosed within a stationary housing or plenumchamber 288 to receive the air discharged radially outward through thefins of the evaporator during which it has been cooled by heat exchangewith the condensed refrigerant in the evaporator tubes. The cooled airdischarged to the plenum chamber 288 is delivered to a duct 290 that isconnected at one end thereof to the distribution duct 282 through a sidewall thereof as indicated at 292. Valve means, such as a shutter 294, isprovided in the distribution duct 282 for selectively admitting air tothe duct 282 from either the condenser exhaust duct 278 or theevaporator exhaust duct 290. For example, with the shutter 294 in theposition shown in FIG. 10 disposed crosswise of the distribution duct282, air is admitted from duct 290 to duct 282 and air from thecondenser exhaust duct 278 is prevented from entering the duct 282. Theother end of the duct 290 is connected to the return duct branch 296through a side wall thereof, as indicated at 290a, and valve means, suchas shutter 290b, is provided for selectively admitting the cooled airfrom duct 290 to duct 296.

Air distributed by the duct 282 and discharged throughout the interiorof the building through one or more of the outlets 284 is returned tothe apparatus by a return duct 298 that divides into two branches 296and 300, respectively, a valve, such as shutter 302 being provided forselectively admitting returning air to branch ducts 296 and 300 asdesired. The branch duct 296 leads from the duct 298 and is connectedinto the fresh air inlet duct 268 through a side wall thereof asindicated at 304. The other branch duct 300 is connected to the fluidinlet chamber of the evaporator and also to the air distribution duct282, a valve, such as shutter 306, being provided for selectivelycontrolling the flow of air to the evaporator inlet or the airdistribution duct 282 as desired.

Referring to FIG. 10 of the drawings, for cooling or air-conditioningthe building in summer or other warm climate, the fresh air inletshutters 274 are open as are the shutters 280 of the condenser exhaustduct 278, and the shutter 294 is positioned, as shown, to open the duct290 and admit cooled air to the distribution duct 282 and close thelatter to air from the condenser exhaust duct 278. Shutter 290b in duct290 is closed thereby preventing discharge of cooled air through branchduct 296 into the branch duct 300. Also, shutter 306 in duct 300 isclosed and shutter 302 is positioned, as shown, to close duct 296 andopen duct 300 so that all air returning through duct 298 is conducted tothe inlet of the evaporator.

In operation of the arrangement shown in FIG. 10, all of the heated airdischarged from the condenser C is exhausted through duct 278 to theoutside atmosphere and does not enter the distribution duct 282. On theother hand, all of the cooled air discharged from the evaporator isdelivered by duct 290 to the duct 282 and distributed thereby to theoutlets 284 located throughout the building. The air discharged into thebuilding is returned to the apparatus through the duct 298. Since theshutter 306 in branch duct 300 is closed, and shutter 302 is closed tobranch duct 296 and open to branch duct 300, all of the air returned bythe duct 298 is delivered by branch duct 300 to the evaporator where itis again cooled and recirculated through the building as described.

For winter or other cold climate operation as shown in FIG. 11, thefresh air inlet shutters 274 are closed as are the condenser externalexhaust shutters 280, and the shutter 294 is positioned to close theduct 290 and allow all of the heated air from the duct 278 to enter thedistribution duct 282. Also, the shutter 302 is closed to branch duct300 and opened to branch duct 296 to admit return air from duct 298 intothe condenser inlet duct 272. Thus, in operation. all of the heated airfrom the condenser C is discharged into the duct 282. A portion of theheated air is distributed to the building outlets 284 and the airreturned by the duct 298 is delivered by branch duct 296 to thecondenser inlet duct 270 to be again heated and recirculated asdescribed. The balance of the heated air is con-- ducted through branchduct 300 to the inlet of the evaporator and the cooled air from theevaporator is discharged through duct 290 into the branch duct 296.

By short-circuiting the evaporator air flow through the condenser asshown in FIG. 11, the evaporator temperature and pressure are raised andthe condenser temperature and pressure are lowered. The reduced pressurerise across the refrigerant compressor combined with a decrease incompressor and housing-condenser-evaporator speed during winteroperation reduces the turbine work load. The low pressure ratio, lowspeed compressor operation serves as an idle condition for thecompressor during winter operation.

Whenever the winter ambient air temperature is greater than theevaporator temperature, it is possible to operate the apparatus as aheat pump. In this mode of operation efficient space heating resultsfrom the addition of the heat rejected by the refrigeration cycle to theheat rejected by the Rankine power cycle. The air duct arrangement willbe similar to that shown in FIG. 11 except that provision is made foroutside air to be admitted and caused to flow through the evaporator.

From the foregoing it will be observed that the present inventionprovides novel closed cycle Rankine engine powered cooling, heating andpower generation apparatus that is of compact unitary construction andcan be manufactured and shipped fully assembled, hermetically sealed andcharged with the desired power and refrigerant fluids. The apparatusprovides isenthalpic expansion of the refrigerant fluid with automaticcontrol of the capacity balance of the refrigerant system, automaticseparation of the refrigerant and power fluids in an efficient two fluidsystem without the use of high speed shaft seals, and the rotarycondenser and evaporator function also as blowers for circulating thecooling and heating fluids independently of other power sources therebyproviding an apparatus that is quiet and efficient in operation. Theapparatus is unique in accomplishing its many functions without the useof valves for controlling the flow of refrigerant fluid or power fluidthereby leading to a more simple and reliable apparatus.

While certain embodiments of the invention have been illustrated anddescribed, it is not intended to limit the invention to suchembodiments, and it is contemplated that changes and modifications maybe made and incorporated as desired or required within the scope of thefollowing claims.

I claim:

1. Rotary closed Rankine cycle engine powered cooling and heatingapparatus utilizing different engine power fluid and refrigerant fluidcomprising.

a cylindrical housing mounted for rotation about the axis thereofincluding an internal power fluid boiler,

means for heating the power fluid in said boiler to generate pressurepower fluid vapor therein,

a power fluid expander in said housing including a coaxial drivingmember rotatably driven at a first predetermined speed by the powerfluid vapor generated in the boiler,

means subdividing the interior of said rotatable housing to provide apower fluid compartment for receiving the power fluid from said expanderand a refrigerant fluid compartment,

a compressor rotatably mounted coaxially in the housing and rotationallydriven by the expander driving member for compressing refrigerant fluidfrom said refrigerant fluid compartment.

a condenser mounted coaxially adjacent one side of the housing androtatable therewith comprising a plurality of axially spaced annularfins having heat exchange tubes extending longitudinally therethrough,

a predetermined number of said condenser heat exchange tubes being incommunication with the power fluid compartment of the housing forreceiving and condensing therein the power fluid vapor from said powerfluid expander,

means for conducting compressed refrigerant fluid from the compressor tothe remainder of said condenser heat exchange tubes for condensing saidcompressed refrigerant fluid therein,

refrigerant expander means in said housing for expanding the refrigerantfluid condensed in said condenser,

means for supplying condensed refrigerant fluid from said condenser tosaid refrigerant expander,

an evaporator mounted coaxially adjacent the other side of the housingfrom said condenser and rotatable therewith comprising a plurality ofaxially spaced annular fins having heat exchange tubes extendinglongitudinally therethrough and arranged to receive and vaporize thereinrefrigerant fluid from the refrigerant expander,

means for returning vaporized refrigerant from said evaporator to saidrefrigerant compartment of the housing,

and means operable to rotationally drive the housing, condenser andevaporator as a unit at a second pre determined speed substantiallyslower than said first predetermined speed and operable to cause agaseous heat exchange fluid to be conveyed and accelerated by viscosityshear forces outwardly between the fins of the condenser and evaporatorto the velocity providing optimum heat exchange between said gaseousfluid and the fluids in the heat exchange tubes of the condenser andevaporator.

2. Apparatus as claimed in claim 1 wherein the refrigerant expandercomprises a plurality of capillary tubes equally spacedcircumferentially of the housing and rotatable therewith, the length ofsaid capillary tubes being correlated to the internal flow area thereofand to the number of said tubes to supply the amount of expandedrefrigerant to the evaporator required to provide the designedrefrigeration capacity of the apparatus.

3. Apparatus as claimed in claim 2 wherein the liquid level ofrefrigerant in the heat exchange tubes of the evaporator is disposed ata greater radial distance from the rotation axis of the housing than therefrigerant heat exchange tubes of the condenser, and the capillaryexpander tubes are operable in response to the pressure drop across saidexpander tubes between the refrigerant condenser and evaporator toautomatically establish and maintain capacity balance in the refrigerantfluid system.

4. Apparatus as claimed in claim 1 comprising means for returning to therefrigerant fluid compartment of the housing refrigerant vapor thatmigrates into the power fluid system and collects in the power fluidcondenser tubes.

5. Apparatus as claimed in claim 1 comprising means for returning to thepower fluid compartment of the housing power fluid that migrates intothe refrigerant fluid system and collects in the evaporator.

6. Apparatus as claimed in claim 5 wherein the rotary housing includesan annular vaporizing chamber and means is provided for delivering tosaid vaporizing chamber power fluid that migrates into the refrigerantfluid system and collects in the evaporator, said vaporizing chamberbeing heated by the boiler to vaporize the power fluid deliveredthereto, and means for returning vaporized power fluid from saidvaporizing chamber to the power fluid compartment of the housing.

7. Apparatus as claimed in claim 1 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises anoccluded fixedratio gear train mounted coaxially within the housing andconnected between the power fluid expander driving member and saidhousing, and torque anchor means cooperable with the occluded gear trainopposing the reaction torque generated thereby so that the full poweroutput of the power fluid expander is transmitted directly to thecompressor and rotary housing.

8. Apparatus as claimed in claim 1 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises rotarypower means mounted externally of the said unit and having a drivingconnection thereto.

9. Apparatus as claimed in claim 1 comprising an alternator mountedcoaxially in the housing having the armature thereof driven by therotatable driving member of the power fluid expander and operable togenerate an electric current, and means for conducting the electriccurrent generated by said alternator to a load located exteriorly of therotary housing-condenserevaporator unit.

10. Apparatus as claimed in claim 1 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises aconstant speed electric motor mounted externally of said unit and havinga driving connection thereto, an alternator is mounted coaxially in thehousing having the armature thereof driven by the rotatable drivingmember of the power fluid expander and operable to generate an electriccurrent, and means is provided for conducting the electric currentgenerated by said alternator externally ofthe rotaryhousing-condenser-evaporator unit to said electric motor.

ll. Apparatus as claimed in claim 1 wherein the condenser meanscomprises separate outer and inner concentrically disposed condensersections respectively for the expander exhaust power fluid andcompressed refrigerant fluid mounted coaxially adjacent one side of thehousing and rotatable therewith, each condenser section comprising aplurality of axially spaced annular fins radially spaced from the finsof the other section to provide a thermal gap therebetween, a pluralityof heat 5 exchange tubes extending longitudinally through the fins ofsaid outer condenser section for condensing the expander exhaust fluidtherein, and a plurality of heat exchange tubes extending longitudinallythrough the fins of the inner condenser section for condensingrefrigerant fluid therein. the expander exhaust and refrigerant fluidsin said heat exchange tubes being condensed by heat exchange with acooling fluid passing radially outward between the tins of saidsections.

12. Apparatus as claimed in claim 11 wherein the fins of the outer andinner condenser sections are disposed in radial alignment with oneanother and the axial spacing between adjacent fins of each section iscorrelated to the speed of rotation thereof and the kinematic viscosityof the cooling fluid to provide a Taylor number operable at the ratio ofthe inner radius of the inner section fins to the outer radius of theouter section fins to convey and accelerate said cooling fluid byviscosity shear forces spirally outward between the fins substantiallyto the velocity providing optimum heat exchange between the coolingfluid and the fluids in said heat exchange tubes to condense saidfluids.

13. Apparatus as claimed in claim 9 comprising means for circulating acooling fluid within the rotary housing in heat exchange relation withthe alternator to cool the same.

14. Apparatus as claimed in claim 9 comprising means for circulating airfrom the ambient atmosphere surrounding the rotary housing interiorly ofsaid housing in heat exchange relation with the alternator to cool thesame.

15. Apparatus as claimed in claim 7 wherein the rotary housing includesa sump compartment for containing an annular bath of lubricant and thetorque anchor means is non-rotatable with the housing and includes pumpmeans operable to pump lubricant inwardly from said annular bath to theexpander driving member to lubricate same.

16. Apparatus as claimed in claim 15 comprising means for delivering tothe lubricant bath in the sump compartment power fluid that migratesinto the refrigerant fluid system and collects in the evaporator, andmeans for returning said power fluid from the lubricant bath to thepower fluid compartment of the housing.

17. Apparatus as claimed in claim 16 wherein the means for returningpower fluid from the lubricant bath to the power fluid compartment ofthe housing includes an annular vaporizing chamber in said housing,means for delivering power fluid from the lubricant bath to saidvaporizing chamber, said vaporizing chamber being heated by the boilerto vaporize the power fluid delivered thereto, and means for returningthe vaporized power fluid from the vaporizing chamber to the power fluidcompartment of the housing.

18. Cooling and heating apparatus as claimed in claim 1 comprising afluid inlet duct connected to the inlet to the condenser fluid chamber,a housing defining a plenum chamber enclosing the condenser forreceiving heated fluid discharged outwardly through the condenser flns,an exhaust duct connected to the condenser plenum chamber to receiveheated fluid therefrom, a fluid distribution duct connected to saidexhaust duct for conducting heated fluid therefrom to a remote zone, areturn duct from said zone terminating in a first branch duct connectedto said air inlet duct to the condenser chamber and a second branch ductconnected to the fluid inlet chamber of the evaporator and to said airdistribution duct, a housing defining a plenum chamber enclosing theevaporator for receiving therefrom cool fluid discharged outwardlythrough the evaporator fins, a cool fluid duct connected to saidevaporator plenum chamber for receiving cool fluid therefrom. said coolfluid duct also being connected to said first return branch duct and tosaid distribution duct, valve means selectively operable for controllingthe flow of fluid respectively from said exhaust duct and said coolfluid duct to the distribution duct, and valve means selectivelyoperable for controlling fluid flow from said return duct to the saidfirst and second branch ducts and between the latter and said cool fluidduct and fluid distribution duct.

19. Apparatus as claimed in claim 3 comprising means for returning tothe refrigerant fluid compartment of the housing refrigerant vapor thatmigrates into the power fluid system and collects in the power fluidcondenser tubes.

20. Apparatus as claimed in claim 3 comprising means for returning tothe power fluid compartment of the housing power fluid that migratesinto the refrigerant fluid system and collects in the evaporator.

21. Apparatus as claimed in claim 3 wherein the rotary housing includesan annular vaporizing chamber and means is provided for delivering tosaid vaporizing chamber power fluid that migrates into the refrigerantfluid system and collects in the evaporator, said vaporizing chamberbeing heated by the boiler to vaporize the power fluid deliveredthereto, and means for returning vaporized power fluid from saidvaporizing chamber to the power fluid compartment of the housing.

22. Apparatus as claimed in claim 3 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises anoccluded fixedratio gear train mounted coaxially within the housing andconnected between the power fluid expander driving member and saidhousing, and torque anchor means cooperable with the occluded gear trainopposing the reaction torque generated thereby so that the full poweroutput of the power fluid expander is trans mitted directly to thecompressor and rotary housing.

23. Apparatus as claimed in claim 3 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises arotary power means mounted externally of the said unit and having adriving connection thereto.

24. Apparatus as claimed in claim 3 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises aconstant speed electric motor mounted externally of said unit and havinga driving connection thereto, an alternator is mounted coaxially in thehousing having the armature thereof driven by the rotatable drivingmember of the power fluid expander and operable to generate an electriccurrent, and means is provided for conducting the electric currentgenerated by said alternator externally of the rotaryhousing-condenser-evaporator unit to said electric power.

25. Apparatus as claimed in claim 24 comprising means for circulatingair from the ambient atmosphere surrounding the rotary housinginteriorly of said housing in heat exchange relation with the alternatorto cool the same.

26. Cooling and heating apparatus as claimed in claim 3 comprising afluid inlet duct connected to the inlet to the condenser fluid chamber,a housing defining a plenum chamber enclosing the condenser forreceiving heated fluid discharged outwardly through the condenser fins,an exhaust duct connected to the condenser plenum chamber to receiveheated fluid therefrom, a fluid distribution duct connected to saidexhaust duct for conducting heated fluid therefrom to a remote zone, areturn duct from said zone terminating in a first branch duct connectedto said air inlet duct to the condenser chamber and a second branch ductconnected to the fluid inlet chamber of the evaporator and to said airdistribution duct, a housing defining a plenum chamber enclosing theevaporator for receiving therefrom cool fluid discharged outwardlythrough the evaporator fins, a cool fluid duct connected to saidevaporator plenum chamber for receiving cool fluid therefrom, said coolfluid duct also being connected to said first return branch duct and tosaid distribution duct, valve means selectively operable for controllingthe flow of fluid respectively from said exhaust duct and said coolfluid duct to the distribution duct, and valve means selectivelyoperable for controlling fluid flow from said return duct to the saidfirst and second branch ducts and between the latter and said cool fluidduct and fluid distribution duct.

27. Apparatus as claimed in claim 3 wherein the con denser meanscomprises separate outer and inner concentrically disposed condensersections respectively for the expander exhaust power fluid andcompressed refrigerant fluid mounted coaxially adjacent one side of thehousing and rotatable therewith, each condenser section comprising aplurality of axially spaced annular fins radially spaced from the finsof the other section to provide a thermal gap therebetween, a pluralityof heat exchange tubes extending longitudinally through the fins of saidouter condenser section for condensing the expander exhaust fluidtherein, and a plurality of heat exchange tubes extending longitudinallythrough the fins of the inner condenser section for condensingrefrigerant fluid therein, the expander exhaust and refrigerant fluidsin said heat exchange tubes being condensed by heat exchange with acooling fluid passing radially outward between the fins of saidsections.

28. Apparatus as claimed in claim 22 wherein the condenser meanscomprises separate outer and inner concentrically disposed condensersections respectively for the expander exhaust power fluid andcompressed refrigerant fluid mounted coaxially adjacent one side of thehousing and rotatable therewith, each condenser section comprising aplurality of axially spaced annular fins radially spaced from the finsof the other section to provide a thermal gap therebetween, a pluralityof heat exchange tubes extending longitudinally through the fins of saidouter condenser section for condensing the expander exhaust fluidtherein, and a plurality of heat exchange tubes extending longitudinallythrough the fins of the inner condenser section for condensingrefrigerant fluid therein, the expander exhaust and refrigerant fluidsin said heat exchange tubes being condensed by heat exchange with acooling fluid passing radially outward between the fins of saidsections.

1. Rotary Rankine cycle engine powered cooling and heating apparatusutilizing different engine power fluid and refrigerant fluid comprising,a cylindrical housing mounted for rotation about the axis thereofincluding an internal power fluid boiler, means for heating the powerfluid in said boiler to generate pressure power fluid vapor therein, apower fluid expander in said housing including a coaxial driving memberrotatably driven at a first predetermined speed by the power fluid vaporgenerated in the boiler, means subdividing the interior of saidrotatable housing to provide a power fluid compartment for receiving thepower fluid from said expander and a refrigerant fluid compartment, acompressor rotatably mounted coaxially in the housing and rotationallydriven by the expander driving member for compressing refrigerant fluidfrom said refrigerant fluid compartment, a condenser mounted coaxiallyadjacent one side of the housing and rotatable therewith comprising aplurality of axially spaced annular fins having heat exchange tubesextending longitudinally therethrough, a predetermined number of saidcondenser heat exchange tubes being in communication with the powerfluid compartment of the housing for receiving and condensing thereinthe power fluid vapor from said power fluid expander, means forconducting compressed refrigerant fluid from the compressor to theremainder of said condenser heat exchange tubes for condensing saidcompressed refrigerant fluid therein, refrigerant expander means in saidhousing for expanding the refrigerant fluid condensed in said condenser,means for supplying condensed refrigerant fluid from said condenser tosaid refrigerant expander, an evaporator mounted coaxially adjacent theother side of the housing from said condenser and rotatable therewithcomprising a plurality of axially spaced annular fins having heatexchange tubes extending longitudinally therethrough and arranged toreceive and vaporize therein refrigerant fluid from the refrigerantexpander, means for returning vaporized refrigerant from said evaporatorto said refrigerant compartment of the housing, and means operable torotationally drive the housing, condenser and evaporator as a unit at asecond predetermined speed substantially slower than said firstpredetermined speed and operable to cause a gaseous heat exchange fluidto be conveyed and accelerated by viscosity shear forces outwardlybetween the fins of the condenser and evaporator to the velocityproviding optimum heat exchange between said gaseous fluid and thefluids in the heat exchange tubes of the condenser and evaporator. 2.Apparatus as claimed in claim 1 wherein the refrigerant expandercomprises a plurality of capillary tubes equally spacedcircumferentially of the housing and rotatable therewith, the length ofsaid capillary tubes being correlated to the internal flow area thereofand to the number of said tubes to supply the amount of expandedrefrigerant to the evaporator required to provide the designedrefrigeration capacity of the apparatus.
 3. Apparatus as claimed inclaim 2 wherein the liquid level of refrigerant in the heat exchangetubes of the evaporator is disposed at a greater radial distance fromthe rotation axis of the housing than the refrigerant heat exchangetubes of the condenser, and the capillary expander tubes are operable inresponse to the pressure drop across said expander tubes between therefrigerant condenser and evaporator to automatically establish andmaintain capacity balance in the refrigerant fluid system.
 4. Apparatusas claimed in claim 1 comprising means for returning to the refrigerantfluid compartment of the housing refrigerant vapor that migrates intothe power fluid system and collects in the power fluid condenser tubes.5. Apparatus as claimed in claim 1 comprising means for returning to thepower fluid compartment of the housing power fluid that migrates intothe refrigerant fluid system and collects in the evaporator. 6.Apparatus as claimed in claim 5 wherein the rotary housing includes anannular vaporizing chamber and means is provided for delivering to saidvaporizing chamber power fluid that migrates into the refrigerant fluidsystem and collects in the evaporator, said vaporizing chamber beingheated by the boiler to vaporize the power fluid delivered thereto, andmeans for returning vaporized power fluid from said vaporizing chamberto the power fluid compartment of the housing.
 7. Apparatus as claimedin claim 1 wherein the means for rotationally driving the housing,condenser and evaporator as a unit comprises an occluded fixed-ratiogear train mounted coaxially within the housing and connected betweenthe power fluid expander driving member and said housing, and torqueanchor means cooperable with the occluded gear train opposing thereaction torque generated thereby so that the full power output of thepower fluid expander is transmitted directly to the compressor androtary housing.
 8. Apparatus as claimed in claim 1 wherein the means forrotationally driving the housing, condenser and evaporator as a unitcomprises rotary power means mounted externally of the said unit andhaving a driving connection thereto.
 9. Apparatus as claimed in claim 1comprising an alternator mounted coaxially in the housing having thearmature thereof driven by the rotatable driving member of the powerfluid expander and operable to generate an electric current, and meansfor conducting the electric current generated by said alternator to aload located exteriorly of the rotary housing-condenser-evaporator unit.10. Apparatus as claimed in claim 1 wherein the means for rotationallydriving the housing, condenser and evaporator as a unit comprises aconstant speed electric motor mounted externally of said unit and havinga driving connection thereto, an alternator is mounted coaxially in thehousing having the armature thereof driven by the rotatable drivingmember of the power fluid expander and operable to generate an electriccurrent, and means is provided for conducting the electric currentgenerated by said alternator externally of the rotaryhousing-condenser-evaporator unit to said electric motor.
 11. Apparatusas claimed in claim 1 wherein the condenser means comprises separateouter and inner concentrically disposed condenser sections respectivelyfor the expander exhaust power fluid and compressed refrigerant fluidmounted coaxially adjacent one side of the housing and rotatablethereWith, each condenser section comprising a plurality of axiallyspaced annular fins radially spaced from the fins of the other sectionto provide a thermal gap therebetween, a plurality of heat exchangetubes extending longitudinally through the fins of said outer condensersection for condensing the expander exhaust fluid therein, and aplurality of heat exchange tubes extending longitudinally through thefins of the inner condenser section for condensing refrigerant fluidtherein, the expander exhaust and refrigerant fluids in said heatexchange tubes being condensed by heat exchange with a cooling fluidpassing radially outward between the fins of said sections. 12.Apparatus as claimed in claim 11 wherein the fins of the outer and innercondenser sections are disposed in radial alignment with one another andthe axial spacing between adjacent fins of each section is correlated tothe speed of rotation thereof and the kinematic viscosity of the coolingfluid to provide a Taylor number operable at the ratio of the innerradius of the inner section fins to the outer radius of the outersection fins to convey and accelerate said cooling fluid by viscosityshear forces spirally outward between the fins substantially to thevelocity providing optimum heat exchange between the cooling fluid andthe fluids in said heat exchange tubes to condense said fluids. 13.Apparatus as claimed in claim 9 comprising means for circulating acooling fluid within the rotary housing in heat exchange relation withthe alternator to cool the same.
 14. Apparatus as claimed in claim 9comprising means for circulating air from the ambient atmospheresurrounding the rotary housing interiorly of said housing in heatexchange relation with the alternator to cool the same.
 15. Apparatus asclaimed in claim 7 wherein the rotary housing includes a sumpcompartment for containing an annular bath of lubricant and the torqueanchor means is non-rotatable with the housing and includes pump meansoperable to pump lubricant inwardly from said annular bath to theexpander driving member to lubricate same.
 16. Apparatus as claimed inclaim 15 comprising means for delivering to the lubricant bath in thesump compartment power fluid that migrates into the refrigerant fluidsystem and collects in the evaporator, and means for returning saidpower fluid from the lubricant bath to the power fluid compartment ofthe housing.
 17. Apparatus as claimed in claim 16 wherein the means forreturning power fluid from the lubricant bath to the power fluidcompartment of the housing includes an annular vaporizing chamber insaid housing, means for delivering power fluid from the lubricant bathto said vaporizing chamber, said vaporizing chamber being heated by theboiler to vaporize the power fluid delivered thereto, and means forreturning the vaporized power fluid from the vaporizing chamber to thepower fluid compartment of the housing.
 18. Cooling and heatingapparatus as claimed in claim 1 comprising a fluid inlet duct connectedto the inlet to the condenser fluid chamber, a housing defining a plenumchamber enclosing the condenser for receiving heated fluid dischargedoutwardly through the condenser fins, an exhaust duct connected to thecondenser plenum chamber to receive heated fluid therefrom, a fluiddistribution duct connected to said exhaust duct for conducting heatedfluid therefrom to a remote zone, a return duct from said zoneterminating in a first branch duct connected to said air inlet duct tothe condenser chamber and a second branch duct connected to the fluidinlet chamber of the evaporator and to said air distribution duct, ahousing defining a plenum chamber enclosing the evaporator for receivingtherefrom cool fluid discharged outwardly through the evaporator fins, acool fluid duct connected to said evaporator plenum chamber forreceiving cool fluid therefrom, said cool fluid duct also beingconnected to said first return branch duct and to said distributionduct, valve means selectIvely operable for controlling the flow of fluidrespectively from said exhaust duct and said cool fluid duct to thedistribution duct, and valve means selectively operable for controllingfluid flow from said return duct to the said first and second branchducts and between the latter and said cool fluid duct and fluiddistribution duct.
 19. Apparatus as claimed in claim 3 comprising meansfor returning to the refrigerant fluid compartment of the housingrefrigerant vapor that migrates into the power fluid system and collectsin the power fluid condenser tubes.
 20. Apparatus as claimed in claim 3comprising means for returning to the power fluid compartment of thehousing power fluid that migrates into the refrigerant fluid system andcollects in the evaporator.
 21. Apparatus as claimed in claim 3 whereinthe rotary housing includes an annular vaporizing chamber and means isprovided for delivering to said vaporizing chamber power fluid thatmigrates into the refrigerant fluid system and collects in theevaporator, said vaporizing chamber being heated by the boiler tovaporize the power fluid delivered thereto, and means for returningvaporized power fluid from said vaporizing chamber to the power fluidcompartment of the housing.
 22. Apparatus as claimed in claim 3 whereinthe means for rotationally driving the housing, condenser and evaporatoras a unit comprises an occluded fixed-ratio gear train mounted coaxiallywithin the housing and connected between the power fluid expanderdriving member and said housing, and torque anchor means cooperable withthe occluded gear train opposing the reaction torque generated therebyso that the full power output of the power fluid expander is transmitteddirectly to the compressor and rotary housing.
 23. Apparatus as claimedin claim 3 wherein the means for rotationally driving the housing,condenser and evaporator as a unit comprises a rotary power meansmounted externally of the said unit and having a driving connectionthereto.
 24. Apparatus as claimed in claim 3 wherein the means forrotationally driving the housing, condenser and evaporator as a unitcomprises a constant speed electric motor mounted externally of saidunit and having a driving connection thereto, an alternator is mountedcoaxially in the housing having the armature thereof driven by therotatable driving member of the power fluid expander and operable togenerate an electric current, and means is provided for conducting theelectric current generated by said alternator externally of the rotaryhousing-condenser-evaporator unit to said electric power.
 25. Apparatusas claimed in claim 24 comprising means for circulating air from theambient atmosphere surrounding the rotary housing interiorly of saidhousing in heat exchange relation with the alternator to cool the same.26. Cooling and heating apparatus as claimed in claim 3 comprising afluid inlet duct connected to the inlet to the condenser fluid chamber,a housing defining a plenum chamber enclosing the condenser forreceiving heated fluid discharged outwardly through the condenser fins,an exhaust duct connected to the condenser plenum chamber to receiveheated fluid therefrom, a fluid distribution duct connected to saidexhaust duct for conducting heated fluid therefrom to a remote zone, areturn duct from said zone terminating in a first branch duct connectedto said air inlet duct to the condenser chamber and a second branch ductconnected to the fluid inlet chamber of the evaporator and to said airdistribution duct, a housing defining a plenum chamber enclosing theevaporator for receiving therefrom cool fluid discharged outwardlythrough the evaporator fins, a cool fluid duct connected to saidevaporator plenum chamber for receiving cool fluid therefrom, said coolfluid duct also being connected to said first return branch duct and tosaid distribution duct, valve means selectively operable for controllingthe flow of fluid respectively from said exhaust duct and said coolfluiD duct to the distribution duct, and valve means selectivelyoperable for controlling fluid flow from said return duct to the saidfirst and second branch ducts and between the latter and said cool fluidduct and fluid distribution duct.
 27. Apparatus as claimed in claim 3wherein the condenser means comprises separate outer and innerconcentrically disposed condenser sections respectively for the expanderexhaust power fluid and compressed refrigerant fluid mounted coaxiallyadjacent one side of the housing and rotatable therewith, each condensersection comprising a plurality of axially spaced annular fins radiallyspaced from the fins of the other section to provide a thermal gaptherebetween, a plurality of heat exchange tubes extendinglongitudinally through the fins of said outer condenser section forcondensing the expander exhaust fluid therein, and a plurality of heatexchange tubes extending longitudinally through the fins of the innercondenser section for condensing refrigerant fluid therein, the expanderexhaust and refrigerant fluids in said heat exchange tubes beingcondensed by heat exchange with a cooling fluid passing radially outwardbetween the fins of said sections.
 28. Apparatus as claimed in claim 22wherein the condenser means comprises separate outer and innerconcentrically disposed condenser sections respectively for the expanderexhaust power fluid and compressed refrigerant fluid mounted coaxiallyadjacent one side of the housing and rotatable therewith, each condensersection comprising a plurality of axially spaced annular fins radiallyspaced from the fins of the other section to provide a thermal gaptherebetween, a plurality of heat exchange tubes extendinglongitudinally through the fins of said outer condenser section forcondensing the expander exhaust fluid therein, and a plurality of heatexchange tubes extending longitudinally through the fins of the innercondenser section for condensing refrigerant fluid therein, the expanderexhaust and refrigerant fluids in said heat exchange tubes beingcondensed by heat exchange with a cooling fluid passing radially outwardbetween the fins of said sections.
 29. Apparatus as claimed in claim 24wherein the condenser means comprises separate outer and innerconcentrically disposed condenser sections respectively for the expanderexhaust power fluid and compressed refrigerant fluid mounted coaxiallyadjacent one side of the housing and rotatable therewith, each condensersection comprising a plurality of axially spaced annular fins radiallyspaced from the fins of the other section to provide a thermal gaptherebetween, a plurality of heat exchange tubes extendinglongitudinally through the fins of said outer condenser section forcondensing the expander exhaust fluid therein, and a plurality of heatexchange tubes extending longitudinally through the fins of the innercondenser section for condensing refrigerant fluid therein, the expanderexhaust and refrigerant fluids in said heat exchange tubes beingcondensed by heat exchange with a cooling fluid passing radially outwardbetween the fins of said sections.
 30. Cooling and heating apparatus asclaimed in claim 28 comprising a fluid inlet duct connected to the inletto the condenser fluid chamber, a housing defining a plenum chamberenclosing the condenser for receiving heated fluid discharged outwardlythrough the condenser fins, an exhaust duct connected to the condenserplenum chamber to receive heated fluid therefrom, a fluid distributionduct connected to said exhaust duct for conducting heated fluidtherefrom to a remote zone, a return duct from said zone terminating ina first branch duct connected to said air inlet duct to the condenserchamber and a second branch duct connected to the fluid inlet chamber ofthe evaporator and to said air distribution duct, a housing defining aplenum chamber enclosing the evaporator for receiving therefrom coolfluid discharged outwardly through the evaporator fins, a cool fluidduct connected to saId evaporator plenum chamber for receiving coolfluid therefrom, said cool fluid duct also being connected to said firstreturn branch duct and to said distribution duct, valve meansselectively operable for controlling the flow of fluid respectively fromsaid exhaust duct and said cool fluid duct to the distribution duct, andvalve means selectively operable for controlling fluid flow from saidreturn duct to the said first and second branch ducts and between thelatter and said cool fluid duct and fluid distribution duct.
 31. Coolingand heating apparatus as claimed in claim 29 comprising a fluid inletduct connected to the inlet to the condenser fluid chamber, a housingdefining a plenum chamber enclosing the condenser for receiving heatedfluid discharged outwardly through the condenser fins, an exhaust ductconnected to the condenser plenum chamber to receive heated fluidtherefrom, a fluid distribution duct connected to said exhaust duct forconducting heated fluid therefrom to a remote zone, a return duct fromsaid zone terminating in a first branch duct connected to said air inletduct to the condenser chamber and a second branch duct connected to thefluid inlet chamber of the evaporator and to said air distribution duct,a housing defining a plenum chamber enclosing the evaporator forreceiving therefrom cool fluid discharged outwardly through theevaporator fins, a cool fluid duct connected to said evaporator plenumchamber for receiving cool fluid therefrom, said cool fluid duct alsobeing connected to said first return branch duct and to saiddistribution duct, valve means selectively operable for controlling theflow of fluid respectively from said exhaust duct and said cool fluidduct to the distribution duct, and valve means selectively operable forcontrolling fluid flow from said return duct to the said first andsecond branch ducts and between the latter and said cool fluid duct andfluid distribution duct.